US8708677B2 - Screw compressor having injection having injection mechanism that injects oil or refrigerant toward a starting end of an extending direction of a helical groove of the female rotor or the male rotor - Google Patents

Screw compressor having injection having injection mechanism that injects oil or refrigerant toward a starting end of an extending direction of a helical groove of the female rotor or the male rotor Download PDF

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US8708677B2
US8708677B2 US12/864,087 US86408709A US8708677B2 US 8708677 B2 US8708677 B2 US 8708677B2 US 86408709 A US86408709 A US 86408709A US 8708677 B2 US8708677 B2 US 8708677B2
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Prior art keywords
rotor
helical groove
oil
helical
screw
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US12/864,087
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US20100329918A1 (en
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Nozomi Gotou
Hideyuki Gotou
Harunori Miyamura
Hideki Fujiwara
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Daikin Industries Ltd
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Daikin Industries Ltd
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Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FUJIWARA, HIDEOKI, GOTOU, NOZOMI, GOTOU, HIDEYUKI, MIYAMURA, HARUNORI
Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. CORRECTIVE ASSIGMMENT TO CORRECT THE 4TH INVENTOR'S FIRST NAME, PREVIOUSLY RECORDED ON REEL 024726 FRAME 0129. ASSIGNOR(S) HEREBY CONFIRMS THE CHANGE. Assignors: FUJIWARA, HIDEKI, GOTOU, NOZOMI, GOTOU, HIDEYUKI, MIYAMURA, HARUNORI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type

Definitions

  • the present invention relates to screw compressors in which oil or refrigerant is injected into compression chambers.
  • compressors for compressing refrigerant or air there have been known single-screw compressors including one screw rotor, a casing for accommodating the screw rotor, and two gate rotors (refer to Japanese Patent Publication No. H02-248678 A).
  • compression chambers are formed by meshing gates of the gate rotors with helical grooves of the screw rotor, and refrigerant is compressed by rotation of the screw rotor and the gate rotors.
  • oil is injected into the compression chambers for the purpose of lubricating the helical grooves and the gates and enhancing sealability of gaps between the helical grooves and the gates.
  • the present invention has been made in view of such circumstances, and an object of the present invention is to prevent mechanical loss from increasing at a time of injecting oil or refrigerant into compression chambers.
  • a screw compressor includes the following: a screw rotor ( 40 ) provided with multiple helical grooves ( 41 , 41 , . . . ); and a gate rotor ( 50 A, 50 B) provided with multiple gates ( 51 , 51 , . . . ) which mesh with the helical grooves ( 41 , 41 , . . . ), in which, in a compression chamber ( 23 ) formed with the helical groove ( 41 ) and the gate ( 51 ), refrigerant taken-in from a starting-end side of the helical groove ( 41 ) is compressed and discharged from a dead-end side of the helical groove ( 41 ).
  • the screw compressor further includes an injection mechanism ( 3 ) for injecting oil or refrigerant from a discharge hole ( 31 a ) thereof into the compression chamber ( 23 ).
  • the injection mechanism ( 3 ) injects oil or refrigerant to the screw rotor ( 40 ) such that rotational torque is imparted in a direction in which the screw rotor ( 40 ) is rotated at a time of compression.
  • oil and the like injected from the injection mechanism ( 3 ) imparts the rotational torque for the rotation in the rotational direction at the time of compression (hereinafter, also referred to as compression rotational direction) to the screw rotor ( 40 ).
  • compression rotational direction the rotational torque for the rotation in the rotational direction at the time of compression
  • injected oil and the like do not resist the rotation of the screw rotor ( 40 ) at the time of compression, but support the rotation thereof.
  • mechanical loss is prevented from increasing, and efficiency of the screw compressor can be enhanced.
  • the injection mechanism ( 3 ) injects oil or refrigerant to a region of the screw rotor ( 40 ) being rotated in which region the helical grooves ( 41 , 41 , . . . ) move in a direction of moving away from the discharge hole ( 31 a ).
  • the screw rotor ( 40 ) is rotated in such a manner that the helical grooves ( 41 , 41 , . . . ) come close to the discharge hole ( 31 a ) in one region, and the screw rotor ( 40 ) is rotated in such a manner that the helical grooves ( 41 , 41 , . . . ) move in a manner of moving away from the discharge hole ( 31 a ) in the other region.
  • the injection mechanism ( 3 ) injects oil and the like to the one region in which the helical grooves ( 41 , 41 , . . . ) move in a manner of moving away from the discharge hole ( 31 a ).
  • a component in a tangential direction of an impact of oil and the like injected from the injection mechanism ( 3 ) and struck to the screw rotor ( 40 ) corresponds to the compression rotational direction of the screw rotor ( 40 ).
  • the rotational torque in the compression rotational direction can be imparted to the screw rotor ( 40 ).
  • mechanical loss is prevented from increasing, and efficiency of the screw compressor can be enhanced.
  • the injection mechanism ( 3 ) injects oil or refrigerant toward, relative to a perpendicular line dropped from the discharge hole ( 31 a ) to the axis (X) of the screw rotor ( 40 ), an end portion on a discharge side of the screw rotor ( 40 ) in an axial direction of the screw rotor ( 40 ).
  • the helical grooves ( 41 , 41 , . . . ) when observed from a point outside of an outer peripheral of the screw rotor ( 40 ), for example, from a point of the discharge hole ( 31 a ) at the time of the rotation of the screw rotor ( 40 ), the helical grooves ( 41 , 41 , . . . ) appear to move from an end portion on an intake side to an end portion on a discharge side in the axial direction of the screw rotor ( 40 ).
  • a screw compressor includes the following: a screw rotor ( 40 ) provided with multiple helical grooves ( 41 , 41 , . . . ); and a gate rotor ( 50 A, 50 B) provided with multiple gates ( 51 , 51 , . . . ) which mesh with the helical grooves ( 41 , 41 , . . . ), in which, in a compression chamber ( 23 ) formed with the helical groove ( 41 ) and the gate ( 51 ), refrigerant taken-in from a starting-end side of the helical groove ( 41 ) is compressed and discharged from a dead-end side of the helical groove ( 41 ).
  • the screw compressor further includes an injection mechanism ( 3 ) for injecting oil or refrigerant from a discharge hole ( 31 a ) thereof into the compression chamber ( 23 ).
  • the injection mechanism ( 3 ) injects oil or refrigerant to one sidewall surface ( 42 ) of sidewall surfaces ( 42 , 43 ) of the helical groove ( 41 ), the one sidewall surface ( 42 ) being formed on a forward side of an advance direction of the gate ( 51 ) meshing with the helical groove ( 41 ).
  • the helical grooves ( 41 , 41 , . . . ) appear to move from an end portion on an intake side to an end portion on a discharge side in the axial direction of the screw rotor ( 40 ).
  • the movement direction corresponds to the advance direction in which the gates ( 51 , 51 , . . . ) meshing with the helical grooves ( 41 , 41 , . . . ) move by the rotation of the screw rotor ( 40 ).
  • a screw compressor includes the following: a screw rotor ( 40 ) provided with multiple helical grooves ( 41 , 41 , . . . ); and a gate rotor ( 50 A, 50 B) provided with multiple gates ( 51 , 51 , . . . ) which mesh with the helical grooves ( 41 , 41 , . . . ), in which, in a compression chamber ( 23 ) formed with the helical groove ( 41 ) and the gate ( 51 ), refrigerant taken-in from a starting-end side of the helical groove ( 41 ) is compressed and discharged from a dead-end side of the helical groove ( 41 ).
  • the screw compressor further includes an injection mechanism ( 303 ) for injecting oil or refrigerant from a discharge hole ( 331 a ) thereof into the compression chamber ( 23 ).
  • the injection mechanism ( 303 ) injects oil or refrigerant toward an starting end of an extending direction in which the helical groove ( 41 ) extends.
  • the screw rotor ( 40 ) is rotated such that the helical grooves ( 41 , 41 , . . . ) mesh with the gate rotor from the starting-end side thereof and are separated from the gate rotor at the dead-end side thereof. That is, the screw rotor ( 40 ) is rotated from the dead-end side to the starting-end side of the helical grooves ( 41 , 41 , . . . ).
  • the screw compressor is configured such that oil from the injection mechanism ( 3 ) is injected in the direction of imparting rotational torque in the compression rotational direction to the screw rotor ( 40 ).
  • oil from the injection mechanism ( 3 ) is injected in the direction of imparting rotational torque in the compression rotational direction to the screw rotor ( 40 ).
  • the screw compressor is configured such that oil from the injection mechanism ( 3 ) is injected to the region of the rotated screw rotor ( 40 ) in which region the helical grooves ( 41 , 41 , . . . ) move in the direction of moving away from the discharge holes ( 31 a , 31 a ).
  • rotational torque can be imparted in a rotational direction in which the helical grooves ( 41 , 41 , . . . ) move in the direction of moving away from the discharge holes ( 31 a , 31 a ), that is, in the very direction in which the screw rotor ( 40 ) is rotated.
  • rotational torque in the compression rotational direction can be imparted to the screw rotor ( 40 ).
  • the screw compressor is configured such that oil and the like from the injection mechanism ( 3 ) is injected toward, relative to the perpendicular line dropped from the discharge hole ( 31 a ) to the axis (X) of the screw rotor ( 40 ), the end portion on the discharge side of the screw rotor ( 40 ) in the axial direction of the screw rotor ( 40 ).
  • an impact of oil and the like can be applied in the direction in which the helical grooves ( 41 , 41 , . . . ) move in the axial direction of the screw rotor ( 40 ) when the screw rotor ( 40 ) is rotated in the compression rotational direction.
  • rotational torque in the compression rotational direction can be imparted to the screw rotor ( 40 ).
  • the screw compressor is configured such that oil and the like from the injection mechanism ( 3 ) is injected to the one sidewall surface ( 42 ) of the sidewall surfaces ( 42 , 43 ) of the helical groove ( 41 ), the one sidewall surface ( 42 ) being formed on the forward side of the advance direction of the gate meshing with the helical groove ( 41 ).
  • an impact of oil and the like can be applied in the direction of moving the one sidewall surface ( 42 ) the helical groove ( 41 ) in the advance direction of the gate.
  • rotational torque in the compression rotational direction can be imparted to the screw rotor ( 40 ).
  • the screw compressor is configured such that oil and the like from the injection mechanisms ( 303 , 303 ) is injected toward the starting end of the extending direction of the helical groove ( 41 ).
  • an impact of oil and the like can be applied in the direction in which the helical grooves ( 41 , 41 , . . . ) are rotated from the dead-end side to the starting-end side of the screw rotor ( 40 ).
  • rotational torque in the compression rotational direction can be imparted to the screw rotor ( 40 ).
  • FIG. 1 is a lateral sectional view of a screw compressor according to a first embodiment of the present invention, the sectional view being taken along the line I-I in FIG. 2 .
  • FIG. 2 is a vertical sectional view of a structure of the main portion of the screw compressor.
  • FIG. 3 is a perspective view of a screw rotor and gate rotors.
  • FIG. 4 is a perspective view of the screw rotor and the gate rotors from another angle.
  • FIG. 5 are plan views illustrating operation of a compression mechanism according to the first embodiment: FIG. 5(A) illustrates an intake process, FIG. 5(B) illustrates an compression process, and FIG. 5(C) illustrates a discharge process.
  • FIG. 6 is a lateral sectional view of a screw compressor according to a second embodiment, the lateral sectional view corresponding to FIG. 1 .
  • FIG. 7 is a plan view of a screw rotor and gate rotors of a screw compressor according to a third embodiment.
  • FIG. 8 are schematic explanatory views illustrating oil injection directions of a twin-screw compressor according to another embodiment: FIG. 8(A) is a plan view thereof, and FIG. 8(B) is a front view thereof.
  • FIG. 9 are schematic explanatory views illustrating oil injection directions of a twin-screw compressor according to still another embodiment: FIG. 9(A) is a plan view thereof, and FIG. 9(B) is a front view thereof.
  • FIG. 10 are schematic explanatory views illustrating oil injection directions of a twin-screw compressor according to yet another embodiment: FIG. 10(A) is a plan view thereof, and FIG. 10(B) is a front view thereof.
  • a screw compressor ( 1 ) according to a first embodiment of the present invention is provided, for the purpose of compressing refrigerant, in a refrigerant circuit which performs a refrigerant cycle.
  • the screw compressor ( 1 ) has a semi-hermetic structure.
  • a compression mechanism ( 20 ) and an electric motor (not shown) for driving the compression mechanism ( 20 ) are accommodated in a single casing ( 10 ).
  • the compression mechanism ( 20 ) is coupled with the electric motor through a drive shaft ( 21 ).
  • the compression mechanism ( 20 ) includes a single screw rotor ( 40 ), a cylindrical wall ( 11 ) constituting a part of the casing ( 10 ) and defining a screw-rotor accommodating chamber ( 12 ) for accommodating the screw rotor ( 40 ), and two gate rotors ( 50 A, 50 B) which mesh with the screw rotor ( 40 ).
  • the screw rotor ( 40 ) is a metal member formed substantially in a columnar shape.
  • multiple helical grooves ( 41 , 41 , . . . ) helically extending from one end to the other end of the screw rotor ( 40 ).
  • the multiple helical grooves ( 41 , 41 , . . . ) are arranged at equal intervals.
  • the screw rotor ( 40 ) rotatably fits to the cylindrical wall ( 11 ), and an outer peripheral surface thereof comes in sliding contact with an inner peripheral surface of the cylindrical wall ( 11 ).
  • the drive shaft ( 21 ) is inserted into the screw rotor ( 40 ), and the screw rotor ( 40 ) and the drive shaft ( 21 ) are coupled with each other through a key ( 22 ).
  • the drive shaft ( 21 ) is arranged coaxially with the screw rotor ( 40 ).
  • a distal end portion of the drive shaft ( 21 ) is rotatably supported by a bearing holder ( 60 ) positioned on a side of the high-pressure spaces (S 2 ) in the compression mechanism ( 20 ) (right side in a case of regarding an axial direction of the drive shaft ( 21 ) of FIG. 2 as a lateral direction).
  • the bearing holder ( 60 ) supports the drive shaft ( 21 ) through ball bearings ( 61 ).
  • each of the helical grooves ( 41 ) of the screw rotor ( 40 ) in an axial direction of the screw rotor ( 40 ) is a starting end (left side in FIG. 4 ), and the other end is a dead end (right side in FIG. 4 ). Further, a peripheral edge portion of the one end surface in the axial direction of the screw rotor ( 40 ) is formed as a tapered surface.
  • the starting end of each of the helical grooves ( 41 ) opens in the tapered surface
  • the dead end of each of the helical grooves ( 41 ) opens in the outer peripheral surface of the screw rotor ( 40 ) without opening in the other end surface in the axial direction thereof.
  • the screw rotor ( 40 ) is fitted into the cylindrical wall ( 11 ) such that the starting-end side thereof is directed toward the low-pressure space (S 1 ) and the dead-end side thereof is directed toward the high-pressure spaces (S 2 ) (refer to FIG. 2 ). That is, starting end portions of the helical grooves ( 41 ) are exposed to the low-pressure space (S 1 ).
  • the starting end portions constitute intake ports ( 24 ) of the compression mechanism ( 20 ).
  • Each of the helical grooves ( 41 ) includes: a first sidewall surface ( 42 ) positioned on a forward side of an advance direction of gates ( 51 ) described below of each of the gate rotors ( 50 A ( 50 B)); a second sidewall surface ( 43 ) positioned on a rearward side of the advance direction of the gates ( 51 ); and a bottom wall surface ( 44 ).
  • the two gate rotors ( 50 A, 50 B) are constituted by an upward gate rotor ( 50 A) whose front surface faces upward, and a downward gate rotor ( 50 B) whose front surface faces downward.
  • Each of the gate rotors ( 50 A ( 50 B)) is a resin member having the multiple gates ( 51 , 51 , . . . ) formed in a rectangular shape.
  • Each of the gate rotors ( 50 A ( 50 B)) is attached to a metal rotor-support member ( 55 ).
  • the rotor-support member ( 55 ) includes a base portion ( 56 ), arm portions ( 57 ), and a shaft portion ( 58 ).
  • the base portion ( 56 ) is formed in a shape of a disk somewhat thick.
  • the arm portions ( 57 ) are provided as many as the gates ( 51 ) of the gate rotor ( 50 A ( 50 B)), and extend radially outward from an outer peripheral surface of the base portion ( 56 ).
  • the shaft portion ( 58 ) is formed in a bar-like shape and provided upright while passing through the base portion ( 56 ).
  • a center axis of the shaft portion ( 58 ) corresponds to a center axis of the base portion ( 56 ).
  • Each of the gate rotors ( 50 A ( 50 B)) is attached to surfaces of the base portion ( 56 ) and the arm portions ( 57 ) on a side opposite to the shaft portion ( 58 ).
  • Each of the arm portions ( 57 ) is held in contact with rear surfaces of the gates ( 51 ).
  • one end portion ( 58 a ) of the shaft portion ( 58 ) projects from the front surface of the gate rotor ( 50 A ( 50 B)). Further, a rotary axis of the gate rotor ( 50 A ( 50 B)) corresponds to the center axis of the shaft portion ( 58 ).
  • the two gate rotors ( 50 A, 50 B) are respectively accommodated in gate-rotor accommodating chambers ( 13 , 13 ) arranged outside the cylindrical wall ( 11 ) axisymmetrically with respect to a rotary axis of the screw rotor ( 40 ).
  • the gate-rotor accommodating chambers ( 13 ) communicate with the low-pressure space (S 1 ).
  • a bearing housing ( 13 a ) constituting part of the casing ( 10 ) is arranged in the gate-rotor accommodating chamber ( 13 ).
  • the bearing housing ( 13 a ) is a cylindrical member provided with a flange ( 13 c ) on a proximal end side thereof, and is inserted from an opening ( 11 a ) of the cylindrical wall ( 11 ) into the gate-rotor accommodating chamber ( 13 ).
  • the flange ( 13 c ) is attached to the cylindrical wall ( 11 ).
  • a lid member ( 13 d ) is attached to the flange ( 13 c ), and the bearing housing ( 13 a ) is formed in a bottomed cylindrical shape.
  • Ball bearings ( 13 b , 13 b ) are respectively provided at two upper and lower points in the bearing housing ( 13 a ).
  • the ball bearings ( 13 b , 13 b ) rotatably support the shaft portion ( 58 ) of the gate rotor ( 50 B).
  • the ball bearings ( 13 b ) constitute a bearing portion.
  • Openings ( 11 b ) for communicating the screw-rotor accommodating chamber ( 12 ) and the respective gate-rotor accommodating chambers ( 13 , 13 ) with each other are formed through the cylindrical wall ( 11 ).
  • the gate rotors ( 50 A ( 50 B)) respectively accommodated in the gate-rotor accommodating chambers ( 13 ) are arranged such that the gates ( 51 , 51 , . . . ) mesh with the helical grooves ( 41 , 41 , . . . ) of the screw rotor ( 40 ) through the openings ( 11 b ) of the cylindrical wall ( 11 ).
  • each of the gate rotors ( 50 A, 50 B) is located adjacent to each other in a horizontal direction with respect to the screw rotor ( 40 ). Further, each of the gate rotors ( 50 A ( 50 B)) is arranged such that the front surface thereof faces a rotational direction of the screw rotor ( 40 ), that is, directed to a tangential direction of the screw rotor ( 40 ).
  • the upward gate rotor ( 50 A) is installed in a posture in which the shaft portion ( 58 ) is directed vertically downward whereas the front surface of the upward gate rotor ( 50 A) is directed vertically upward
  • the downward gate rotor ( 50 B) is installed in a posture in which the shaft portion ( 58 ) is directed vertically upward whereas the front surface of the downward gate rotor ( 50 B) is directed vertically downward.
  • the gates ( 51 ) of the gate rotor ( 50 A ( 50 B)) mesh with the helical grooves ( 41 ) of the screw rotor ( 40 ).
  • compression chambers ( 23 ) are formed by closed spaces surrounded by the inner peripheral surface of the cylindrical wall ( 11 ), the helical grooves ( 41 ), and the gates ( 51 ). That is, the compression chambers ( 23 ) are formed by closing tubular spaces surrounded by the helical grooves ( 41 ) and the cylindrical wall ( 11 ), with the gates ( 51 ) from the starting-end side of and/or the dead-end side of the helical grooves ( 41 ).
  • the screw compressor ( 1 ) is provided with slide valves ( 7 ) as capacity control mechanisms.
  • the slide valves ( 7 ) are provided in slide-valve accommodating chambers ( 14 ) formed of outward-swelling shape at two positions in a circumferential direction of the cylindrical wall ( 11 ).
  • Each of the slide valves ( 7 ) has an inner surface constituting part of the inner peripheral surface of the cylindrical wall ( 11 ), and is configured to be slidable in an axial direction of the cylindrical wall ( 11 ).
  • a discharge path ( 17 ) is formed on an outer peripheral surface side of each of the slide valves ( 7 ).
  • the discharge paths ( 17 ) communicate with the high-pressure spaces (S 2 ).
  • the slide valves ( 7 ) are provided with a discharge port ( 73 ) for communicating the compression chambers ( 23 ) and the discharge paths ( 17 ) with each other.
  • bypass paths ( 19 ) are formed in portions on the outer peripheral surface side of the slide valves ( 7 ) and near the low-pressure space (S 1 ).
  • the bypass paths ( 19 ) communicate with the low-pressure space (S 1 ).
  • an axial gap is formed between an end surface ( 16 c ) of the slide-valve accommodating chambers ( 14 ) and an end surface ( 71 c ) of the slide valves ( 7 ).
  • the axial gap communicates with the bypass path ( 19 ), and constitutes a bypass port ( 19 a ) for returning refrigerant from the compression chamber ( 23 ) to the low-pressure space (S 1 ).
  • capacity of the compression mechanism ( 20 ) varies.
  • the screw compressor ( 1 ) is provided with a slide-valve drive mechanism ( 80 ) for slide-driving the slide valves ( 7 ).
  • the slide-valve drive mechanism ( 80 ) includes: a cylinder ( 81 ) fixed to the bearing holder ( 60 ), a piston ( 82 ) loaded in the cylinder ( 81 ), an arm ( 84 ) coupled with a piston rod ( 83 ) of the piston ( 82 ), coupling rods ( 85 ) for coupling the arm ( 84 ) and the slide valves ( 7 ) with each other, and springs ( 86 ) for biasing the arm ( 84 ) in the right direction in FIG. 2 .
  • an inner pressure in a left space of the piston ( 82 ) (space on the screw rotor ( 40 ) side of the piston ( 82 )) is higher than an inner pressure in a right space of the piston ( 82 ) (space on the arm ( 84 ) side of the piston ( 82 )) in FIG. 2 .
  • the slide-valve drive mechanism ( 80 ) is configured to regulate positions of the slide valves ( 7 ) by controlling the inner pressure in the right space of the piston ( 82 ) (that is, gas pressure in the right space).
  • oil-supply mechanisms ( 3 , 3 ) for supplying oil to the screw rotor ( 40 ) and the respective gate rotors ( 50 A, 50 B) are formed in the cylindrical wall ( 11 ) of the casing ( 10 ).
  • Each of the oil-supply mechanisms ( 3 ) constitutes an injection mechanism.
  • each of the oil-supply mechanisms ( 3 ) includes an oil tank (not shown) for storing high-pressure oil, and an oil-supply path ( 30 ) for communicating the oil tank and the screw-rotor accommodating chamber ( 12 ) with each other.
  • the oil tank stores oil separated from refrigerant discharged from the compression chambers ( 23 ).
  • the oil is in a high-pressure state due to discharge pressure of high-pressure refrigerant.
  • the oil-supply path ( 30 ) includes a first path ( 31 ) provided by drilling from an outside of the casing ( 10 ) and opening into the screw-rotor accommodating chamber ( 12 ), and a second path ( 32 ) extending in the axial direction in the casing ( 10 ) and having an upstream end communicating with the oil tank (not shown) and a downstream end communicating with the first path ( 31 ).
  • a discharge hole ( 31 a ) having inner diameter downsized in comparison with that of a midpoint of the first path ( 31 ) and opening to the screw-rotor accommodating chamber ( 12 ).
  • the discharge hole ( 31 a ) is formed at a position which is a midpoint between the two gate rotors ( 50 A, 50 B) in the circumferential direction of the cylindrical wall ( 11 ), and opens the helical groove ( 41 ) immediately after mesh of the gate ( 51 ) (refer to FIG. 5 ) in the axial direction of the cylindrical wall ( 11 ).
  • the other end portion of the first path ( 31 ) on an outer side of the casing ( 10 ) is sealed with a plug ( 31 b ).
  • an axial line of the first path ( 31 ) is inclined, relative to a straight line connecting the discharge hole ( 31 a ) to the axis (X) of the screw rotor ( 40 ), toward a region of the screw rotor ( 40 ) rotated in a compression direction, in which region the helical grooves ( 41 ) move in a direction of moving away from the discharge hole ( 31 a ) (in other words, toward the gate rotors ( 50 A ( 50 B)) meshing with the helical grooves ( 41 ) from the starting-end side thereof).
  • the screw rotor ( 40 ) When the electric motor is activated in the single-screw compressor ( 1 ), the screw rotor ( 40 ) is rotated in accordance with rotation of the drive shaft ( 21 ).
  • the gate rotors ( 50 A, 50 B) are also rotated in accordance with the rotation of the screw rotor ( 40 ), and the compression mechanism ( 20 ) repeats the intake process, the compression process, and the discharge process.
  • the helical groove ( 41 ) illustrated by hatching that is, the intake port ( 24 ) of the compression chamber ( 23 ) opens to the low-pressure space (S 1 ).
  • the helical groove ( 41 ) in which the compression chamber ( 23 ) is formed is meshed with the gate ( 51 ) of the downward gate rotor ( 50 B) positioned on a lower side in FIG. 5(A) .
  • the gate ( 51 ) relatively move to the dead ends of the helical grooves ( 41 ), and capacity of the compression chamber ( 23 ) is increased in accordance therewith.
  • the low-pressure gas refrigerant in the low-pressure space (S 1 ) is sucked into the compression chamber ( 23 ) through the intake port ( 24 ).
  • the screw rotor ( 40 ) When being further rotated, the screw rotor ( 40 ) enters a state of FIG. 5(B) .
  • the compression chamber ( 23 ) illustrated by hatching becomes closed-off.
  • the helical groove ( 41 ) in which the compression chamber ( 23 ) is formed is meshed with the gate ( 51 ) of the upward gate rotor ( 50 A) positioned on an upper side in FIG. 5(B) , and is partitioned with the gates ( 51 ) from the low-pressure space ( 51 ).
  • the gates ( 51 ) move to the dead ends of the helical grooves ( 41 ) in accordance with the rotation of the screw rotor ( 40 )
  • the capacity of the compression chamber ( 23 ) is gradually reduced.
  • the gas refrigerant in the compression chamber ( 23 ) is compressed.
  • the screw rotor ( 40 ) When being still further rotated, the screw rotor ( 40 ) enters a state of FIG. 5(C) .
  • the compression chamber ( 23 ) illustrated by hatching opens to the discharge port ( 73 ), and enters a state of communicating with the high-pressure space (S 2 ) through the discharge port ( 73 ).
  • the compressed gas refrigerant flows out into the discharge path ( 17 ) from the discharge port ( 73 ), and flows in the discharge path ( 17 ) so as to flow out into the high-pressure space (S 2 ).
  • the gate ( 51 ) moves to the dead ends of the helical grooves ( 41 ) in accordance with the rotation of the screw rotor ( 40 ).
  • an opening area of the helical groove ( 41 ) to the discharge port ( 73 ) is increased, whereby the compressed gas refrigerant is pushed out from the helical groove ( 41 ).
  • the compression chamber ( 23 ) relatively move from the starting-end side to the dead-end side of the helical grooves ( 41 ) in the axial direction of the screw rotor ( 40 ) in accordance with the rotation of the screw rotor ( 40 ).
  • the compression chamber ( 23 ) which moves in this manner arrives at the position of the discharge hole ( 31 a ) opening in the cylindrical wall ( 11 ) (refer to FIG. 5(B) ).
  • An intake pressure in the compression chamber ( 23 ) immediately after being closed-off is equal to an intake pressure in the low-pressure space (S 1 ).
  • the oil in the oil tanks passes through the second path ( 32 ) and the first path ( 31 ) and then is injected into the compression chamber ( 23 ) from the discharge hole ( 31 a ).
  • the oil injected into the compression chamber ( 23 ) is sprayed to wall surfaces of the helical groove ( 41 ) and the inner peripheral surface of the cylindrical wall ( 11 ), and flows through the compression chamber ( 23 ) to the gate ( 51 ), with the result of being sprayed also to the gate ( 51 ).
  • the helical groove ( 41 ) and the gate ( 51 ) are lubricated, and a gap between the helical groove ( 41 ) and the gate ( 51 ) is filled with the oil, to thereby enhance sealability.
  • an injection direction of the oil injected from the discharge hole ( 31 a ) is directed to the region of the screw rotor ( 40 ) rotated in the compression direction, in which region the helical grooves ( 41 ) move in the direction of moving away from the discharge hole ( 31 a ) (in other words, toward the gate rotor ( 50 A ( 50 B)) meshing with the helical groove ( 41 ) from the starting-end side thereof)(refer to FIG. 1 ).
  • the oil injected into the compression chamber ( 23 ) flows in a direction substantially the same as a compression rotational direction of the screw rotor ( 40 ).
  • the oil injected into the compression chamber ( 23 ) is prevented from hindering the rotation of the screw rotor ( 40 ) at the time of compression by setting the injection direction of the oil injected from the discharge hole ( 31 a ) to be directed to the region of the screw rotor ( 40 ) rotated in the compression rotational direction, in which region the helical grooves ( 41 ) move in the direction of moving away from the discharge hole ( 31 a ). That is, mechanical loss of the screw compressor ( 1 ) is prevented from increasing.
  • the injection direction of the oil be set such that the oil injected from the discharge hole ( 31 a ) is directed to, of the side walls ( 42 , 43 ) of the helical groove ( 41 ), the first sidewall surface ( 42 ) positioned on the forward side of the advance direction of the gates ( 51 ).
  • the helical grooves ( 41 ) When the helical grooves ( 41 ) are observed from a point on an outer side of the screw rotor ( 40 ), for example, from a point of the discharge hole ( 31 a ) at the time of the rotation of the screw rotor ( 40 ) in the compression rotational direction, the helical grooves ( 41 ) appear to move from an end portion on an intake side to an end portion on a discharge side in the axial direction of the screw rotor ( 40 ).
  • the direction of from the intake-side end portion to the discharge-side end portion in the axial direction of the screw rotor ( 40 ) substantially corresponds to the direction to the forward side of the advance direction of the gates ( 51 ).
  • an impact component for moving the helical grooves ( 41 ) to the forward side of the advance direction of the gates ( 51 ), that is, for moving the helical grooves ( 41 ) in the direction of from the intake-side end portion to the discharge-side end portion in the axial direction of the screw rotor ( 40 ) can be imparted to the screw rotor ( 40 ). That is, rotational torque for rotating the screw rotor ( 40 ) in the compression rotational direction can be imparted.
  • the oil be injected to the bottom wall surface ( 44 ) and be not injected to the second sidewall surface ( 43 ). That is, it is only necessary that the injection direction of oil injected from the discharge hole ( 31 a ) is set as follows: immediately after the discharge hole ( 31 a ) closed by the ridge portion between the two adjacent helical grooves ( 41 , 41 ) opens to the compression chamber ( 23 ) in accordance with relative parallel movement of the helical grooves ( 41 ) and the discharge hole ( 31 a ) in accordance with the rotation of the screw rotor ( 40 ), oil is injected to the first sidewall surface ( 42 ).
  • the screw compressor ( 201 ) according to the second embodiment has oil-supply mechanisms ( 203 ) provided at different positions as those of the oil-supply mechanisms ( 3 ) according to the first embodiment.
  • the components same as those in the first embodiment are denoted by the same reference symbols such that the description thereof is omitted, and description is made mainly of a different configuration.
  • the oil-supply mechanism ( 203 ) has a discharge hole ( 231 a ) formed near the gate rotor ( 50 A ( 50 B)). That is, the oil-supply mechanism ( 203 ) is configured to inject oil to meshing portions between the gates ( 51 ) and the helical grooves ( 41 ).
  • a first path ( 231 ) is formed such that axial lines thereof extend, parallel to a tangential direction of the screw rotor ( 40 ) at a meshing position of the gate ( 51 ) and the helical groove ( 41 ), at a radially inner position relative to the outer peripheral surface of the screw rotor ( 40 ) (that is, relative to an outer peripheral surface of the ridge portion between two adjacent helical grooves ( 41 , 41 )) at the meshing position.
  • the slide valve ( 7 ) exists at the position.
  • the first path ( 231 ) includes a casing-side path ( 233 ) formed by passing through the casing ( 10 ), and a valve-side path ( 234 ) formed by passing through the slide valve ( 7 ) and communicating with the casing-side path ( 233 ).
  • a discharge hole ( 231 a ) is formed at a downstream end of the valve-side path ( 234 ).
  • the slide valve ( 7 ) moves in the axial direction of the screw rotor ( 40 ), and hence the downstream end of the casing-side path ( 233 ) and/or an upstream end of the valve-side path ( 234 ) is enlarged in the axial direction of the screw rotor ( 40 ).
  • the end portions are not necessarily formed in a shape of an elongated hole, but may be merely increased in diameter.
  • the axial line of the first path ( 231 ) is inclined, relative to a straight line connecting the discharge hole ( 231 a ) to the axis (X) of the screw rotor ( 40 ), toward a region of the screw rotor ( 40 ) rotated in the compression direction, in which region the helical grooves ( 41 ) move in a direction of moving away from the discharge hole ( 231 a ) when viewed from the axial direction of the screw rotor ( 40 ).
  • the second embodiment provides the same functions and advantages as those according to the first embodiment.
  • the screw compressor ( 301 ) according to the third embodiment has oil-supply mechanisms ( 303 ) provided at different positions as those of the oil-supply mechanisms ( 3 ) according to the first embodiment.
  • the components same as those in the first embodiment are denoted by the same reference symbols such that the description thereof is omitted, and description is made mainly of a different configuration.
  • the oil-supply mechanism ( 303 ) is configured such that oil injected from discharge hole ( 331 a ) is directed toward the starting end of the extending direction of the helical grooves ( 41 ).
  • the discharge hole ( 331 a ) of the first path ( 331 ) is formed a position which is a midpoint between the two gate rotors ( 50 A, 50 B) in the circumferential direction of the cylindrical wall ( 11 ), and opens the helical groove ( 41 ) immediately after mesh of the gate ( 51 ) in the axial direction of the cylindrical wall ( 11 ).
  • the first path ( 331 ) is configured such that the axial line thereof extends in the extending direction of the helical groove ( 41 ) at a position of the discharge hole ( 331 a ) and that oil is injected toward the starting end of the helical groove ( 41 ).
  • the screw rotor ( 40 ) when the screw rotor ( 40 ) is rotated, the helical groove ( 41 ) meshes with the gate ( 51 ) from the starting-end side thereof and are separated from the gate ( 51 ) at the dead-end side thereof That is, the screw rotor ( 40 ) is rotated from the dead-end side to the starting-end side of the helical groove ( 41 ) at the time of compression.
  • the oil can be injected along the compression rotational direction of the screw rotor ( 40 ).
  • the axial line of the first path ( 331 ) may extend to the bottom wall surface ( 44 ) of the helical groove ( 41 ), or may extend to the inner peripheral surface side of the cylindrical wall ( 11 ) relative to a tangential line drawn from the discharge hole ( 331 a ) to the bottom wall surface ( 44 ).
  • the screw compressors according to the first to third embodiments are configured such that oil is injected into the compression chambers ( 23 ), this should not be construed restrictively.
  • the same configuration can be adopted even for so-called economizer-type screw compressors in which gas refrigerant with an intermediate pressure is injected into compression chambers ( 23 ).
  • the same configuration can be adopted even for screw compressors in which liquid refrigerant is injected into the compression chambers ( 23 ).
  • the axial lines of the first paths ( 31 , 231 ), that is, the injection directions from the discharge holes ( 31 a , 231 a ) extend on the plane perpendicular to the axis of the screw rotor ( 40 ), this should not be construed restrictively.
  • the injection directions may be inclined relative to the perpendicular lines dropped respectively from the discharge holes ( 31 a , 231 a ) to the axis (X) of the screw rotor ( 40 ) such that an upstream side of the injection directions is positioned on an intake end-portion side in the axial direction of the screw rotor ( 40 ) and that a downstream side of the injection directions is positioned on a discharge end-portion side in the axial direction of the screw rotor ( 40 ). That is, as described above, the helical grooves ( 41 ) move parallel from the intake end portion to the discharge end portion in the axial direction of the screw rotor ( 40 ) in accordance with the rotation of the screw rotor ( 40 ).
  • a twin-screw compressor ( 401 ) includes an male rotor ( 440 ) as a screw rotor, a female rotor ( 450 ) as another screw rotor, and a casing (not shown) for accommodating the male rotor ( 440 ) and the female rotor ( 450 ).
  • Multiple helical walls ( 444 , 444 , . . . ) are formed on an outer peripheral surface of the male rotor ( 440 ), and a helical groove ( 441 ) is formed between each pair of the helical walls ( 444 , 444 ).
  • the male rotor ( 440 ) and the female rotor ( 450 ) are arranged in the casing (not shown) such that drive shafts ( 421 , 521 ) thereof are parallel to each other and helical walls ( 444 , 454 ) thereof mesh with each other.
  • the twin-screw compressor ( 401 ) configured as described above includes male-side and female-side oil-supply mechanisms ( 403 , 403 ) for supplying oil to the male rotor ( 440 ) and the female rotor ( 450 ), respectively.
  • the male-side and female-side oil-supply mechanisms ( 403 , 403 ) are arranged such that axial lines of first paths ( 431 , 431 ) thereof are aligned straight with each other on a plane parallel to a plane including an axis of the male rotor ( 440 ) and an axis of the female rotor ( 450 ).
  • the axial lines of each of the first paths ( 431 ) is parallel to a tangential direction of the outer peripheral surface (outer peripheral surfaces of the helical grooves and bottom surfaces of the helical grooves) around the axial center of each of the rotors ( 440 ( 450 )). That is, when viewed from the direction perpendicular to the plane including the axial center of the male rotor ( 440 ) and the axial center of the female rotor ( 450 ), the axial lines of the first paths ( 431 ) are respectively perpendicular to the axial centers of the rotors ( 440 ( 450 )).
  • oil is injected from a discharge hole ( 431 a ) of the male-side oil-supply mechanism ( 403 ) to the helical grooves ( 441 ) of the male rotor ( 440 ), and oil is injected from a discharge hole ( 431 a ) of the female-side oil-supply mechanism ( 403 ) to the helical grooves ( 451 ) of the female rotor ( 450 ).
  • the oil-supply mechanisms ( 403 ) respectively inject oil in directions in which the rotors ( 440 ( 450 )) are rotated, in other words, inject oil to a region in which the respective helical grooves ( 441 ( 451 )) of the rotors ( 440 ( 450 )) move in a direction of moving away from the discharge holes ( 431 a ).
  • the injection directions of oil injected from the discharge holes ( 431 a , 431 a ) are directed to the region in which the helical grooves ( 441 , 451 ) move in the direction of moving away from the respective discharge holes ( 431 a , 431 a ), the region being in the male rotor ( 440 ) and the female rotor ( 450 ) which are rotated in the compression rotational direction.
  • oil injected into the compression chambers is prevented from hindering rotations of the male rotor ( 440 ) and the female rotor ( 450 ) at the time of compression. That is, mechanical loss of the twin-screw compressor ( 401 ) is prevented from increasing.
  • the twin-screw compressor ( 401 ) may be configured as follows: oil from a discharge hole ( 531 a ) of a male-side oil-supply mechanism ( 503 ) is injected to a first sidewall surface ( 442 ) of sidewall surfaces ( 442 , 443 ) of the helical groove ( 441 ) of the male rotor ( 440 ), the first sidewall surface ( 442 ) being positioned on a forward side of an axial advance direction of the helical grooves ( 441 ); similarly, oil from a discharge hole ( 531 a ) of a female-side oil-supply mechanism ( 503 ) is injected to a first sidewall surface ( 452 ) of sidewall surfaces ( 452 , 453 ) of the helical groove ( 451 ) of the female rotor ( 450 ), the first sidewall surface ( 452 ) being positioned on a forward side of an axial advance direction of the helical grooves
  • impact components in a direction of from intake-side end portions to discharge-side end portions in axial directions of the male rotor ( 440 ) and the female rotor ( 450 ) can be imparted to the male rotor ( 440 ) and the female rotor ( 450 ), respectively. That is, rotational torque for rotating the male rotor ( 440 ) and the female rotor ( 450 ) in the compression rotational direction can be imparted.
  • the twin-screw compressor ( 401 ) may be configured as follows: oil from a discharge hole ( 631 a ) of a male-side oil-supply mechanism ( 603 ) is injected to a starting-end side of the helical groove ( 441 ) along an extending direction of the helical groove ( 441 ) of the male rotor ( 440 ); similarly, oil from a discharge hole ( 631 a ) of a female-side oil-supply mechanism ( 603 ) is injected to a dead-end side of the helical groove ( 451 ) along an extending direction of the helical groove ( 451 ) of the female rotor ( 450 ).
  • the oil can be injected in a direction along the compression rotational directions of the male rotor ( 440 ) and the female rotor ( 450 ).
  • mechanical loss caused by injection of oil into compression chambers is prevented from increasing.
  • rotational torque can be imparted to the screw rotor ( 440 ) and the female rotor ( 450 ) in directions of from the dead-end sides to the starting-end sides of the helical grooves ( 441 , 451 ), and hence efficiency of the screw compressor ( 401 ) can be enhanced.
  • the present invention is suitable to screw compressors in which oil or gas is supplied into compression chambers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US12/864,087 2008-01-23 2009-01-23 Screw compressor having injection having injection mechanism that injects oil or refrigerant toward a starting end of an extending direction of a helical groove of the female rotor or the male rotor Expired - Fee Related US8708677B2 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020165561A1 (fr) * 2019-02-11 2020-08-20 J & E Hall Limited Compresseur à vis
US10876531B2 (en) 2018-12-26 2020-12-29 Trane International Inc. Lubricant injection for a screw compressor
US12546316B1 (en) * 2024-08-07 2026-02-10 Copeland Industrial Lp Low ratio oil injection port for applications without the requirement of an oil pump

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9057373B2 (en) 2011-11-22 2015-06-16 Vilter Manufacturing Llc Single screw compressor with high output
WO2013078132A1 (fr) * 2011-11-22 2013-05-30 Vilter Manufacturing Llc Appareil de detente/compression monovis
JP5527396B1 (ja) * 2012-12-17 2014-06-18 ダイキン工業株式会社 スクリュー圧縮機
WO2015114846A1 (fr) * 2014-01-29 2015-08-06 三菱電機株式会社 Compresseur à vis
US20200003211A1 (en) 2017-02-09 2020-01-02 Daikin Industries, Ltd. Screw compressor
US10895259B2 (en) 2018-04-20 2021-01-19 Trane International Inc. Screw compressor having synchronized economizer ports
JP7356044B2 (ja) * 2021-03-31 2023-10-04 ダイキン工業株式会社 スクリュー圧縮機、および冷凍装置
EP4484752A4 (fr) 2022-03-23 2025-05-28 Daikin Industries, Ltd. Compresseur à vis et congélateur
CN115045833B (zh) * 2022-06-22 2023-06-16 好米动力设备有限公司 一种双螺杆三星轮压缩机
WO2025062554A1 (fr) * 2023-09-21 2025-03-27 三菱電機株式会社 Compresseur à vis

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4070166A (en) * 1975-01-24 1978-01-24 Atlas Copco Aktiebolag Method and device for driving liquid from a liquid separator
JPH02248678A (ja) 1989-03-20 1990-10-04 Daikin Ind Ltd スクリュー圧縮機
US5174741A (en) * 1991-04-12 1992-12-29 Kabushiki Kaisha Kobe Seiko Sho Liquid injecting type oil-free screw compressor
JPH05106572A (ja) 1991-10-17 1993-04-27 Daikin Ind Ltd 一軸形スクリユー圧縮機
JPH09151870A (ja) 1995-12-04 1997-06-10 Hitachi Ltd 油冷式スクリュー圧縮機
JP2004162540A (ja) * 2002-11-11 2004-06-10 Kobe Steel Ltd スクリュ圧縮機
JP2008267222A (ja) 2007-04-18 2008-11-06 Kobe Steel Ltd 液冷式スクリュ圧縮機

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3133695A (en) * 1960-06-22 1964-05-19 Zimmern Fernand Compressors
US3752606A (en) * 1971-12-14 1973-08-14 B Zimmern Liquid injection system for globoid-worm compressor
JPS5930919B2 (ja) * 1974-12-24 1984-07-30 北越工業 （株） 液冷式回転圧縮機の液量及び気体容量調整装置
US4227867A (en) * 1978-03-06 1980-10-14 Chicago Pneumatic Tool Company Globoid-worm compressor with single piece housing
JP2001090684A (ja) * 1999-09-22 2001-04-03 Daikin Ind Ltd スクリュー圧縮機および冷凍装置
DE10258145A1 (de) * 2002-12-03 2004-06-24 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4070166A (en) * 1975-01-24 1978-01-24 Atlas Copco Aktiebolag Method and device for driving liquid from a liquid separator
JPH02248678A (ja) 1989-03-20 1990-10-04 Daikin Ind Ltd スクリュー圧縮機
US5174741A (en) * 1991-04-12 1992-12-29 Kabushiki Kaisha Kobe Seiko Sho Liquid injecting type oil-free screw compressor
JPH05106572A (ja) 1991-10-17 1993-04-27 Daikin Ind Ltd 一軸形スクリユー圧縮機
JPH09151870A (ja) 1995-12-04 1997-06-10 Hitachi Ltd 油冷式スクリュー圧縮機
JP2004162540A (ja) * 2002-11-11 2004-06-10 Kobe Steel Ltd スクリュ圧縮機
JP2008267222A (ja) 2007-04-18 2008-11-06 Kobe Steel Ltd 液冷式スクリュ圧縮機

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10876531B2 (en) 2018-12-26 2020-12-29 Trane International Inc. Lubricant injection for a screw compressor
WO2020165561A1 (fr) * 2019-02-11 2020-08-20 J & E Hall Limited Compresseur à vis
US12546316B1 (en) * 2024-08-07 2026-02-10 Copeland Industrial Lp Low ratio oil injection port for applications without the requirement of an oil pump
US20260043404A1 (en) * 2024-08-07 2026-02-12 Copeland Industrial Lp Low ratio oil injection port for applications without the requirement of an oil pump

Also Published As

Publication number Publication date
CN101925745A (zh) 2010-12-22
EP2246571A1 (fr) 2010-11-03
EP2246571A4 (fr) 2014-11-26
CN101925745B (zh) 2013-04-10
WO2009093469A1 (fr) 2009-07-30
JP2009197794A (ja) 2009-09-03
JP4315237B1 (ja) 2009-08-19
US20100329918A1 (en) 2010-12-30

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